EP0751356A2 - Klimaanlage - Google Patents

Klimaanlage Download PDF

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Publication number
EP0751356A2
EP0751356A2 EP96110225A EP96110225A EP0751356A2 EP 0751356 A2 EP0751356 A2 EP 0751356A2 EP 96110225 A EP96110225 A EP 96110225A EP 96110225 A EP96110225 A EP 96110225A EP 0751356 A2 EP0751356 A2 EP 0751356A2
Authority
EP
European Patent Office
Prior art keywords
refrigerant
temperature
supercooling degree
outlet
detecting means
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP96110225A
Other languages
English (en)
French (fr)
Other versions
EP0751356A3 (de
EP0751356B1 (de
Inventor
Kunio c/o Nippondenso Co. Ltd. Iritani
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Denso Corp
Original Assignee
NipponDenso Co Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from JP15959395A external-priority patent/JP3063574B2/ja
Priority claimed from JP16055795A external-priority patent/JP3063575B2/ja
Application filed by NipponDenso Co Ltd filed Critical NipponDenso Co Ltd
Publication of EP0751356A2 publication Critical patent/EP0751356A2/de
Publication of EP0751356A3 publication Critical patent/EP0751356A3/de
Application granted granted Critical
Publication of EP0751356B1 publication Critical patent/EP0751356B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
    • B60H1/00—Heating, cooling or ventilating [HVAC] devices
    • B60H1/32—Cooling devices
    • B60H1/3204—Cooling devices using compression
    • B60H1/3205—Control means therefor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F11/00—Control or safety arrangements
    • F24F11/30—Control or safety arrangements for purposes related to the operation of the system, e.g. for safety or monitoring
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F11/00—Control or safety arrangements
    • F24F11/30—Control or safety arrangements for purposes related to the operation of the system, e.g. for safety or monitoring
    • F24F11/46—Improving electric energy efficiency or saving
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F11/00—Control or safety arrangements
    • F24F11/62—Control or safety arrangements characterised by the type of control or by internal processing, e.g. using fuzzy logic, adaptive control or estimation of values
    • F24F11/63—Electronic processing
    • F24F11/65—Electronic processing for selecting an operating mode
    • F24F11/67—Switching between heating and cooling modes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F11/00—Control or safety arrangements
    • F24F11/70—Control systems characterised by their outputs; Constructional details thereof
    • F24F11/72—Control systems characterised by their outputs; Constructional details thereof for controlling the supply of treated air, e.g. its pressure
    • F24F11/74—Control systems characterised by their outputs; Constructional details thereof for controlling the supply of treated air, e.g. its pressure for controlling air flow rate or air velocity
    • F24F11/77—Control systems characterised by their outputs; Constructional details thereof for controlling the supply of treated air, e.g. its pressure for controlling air flow rate or air velocity by controlling the speed of ventilators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F11/00—Control or safety arrangements
    • F24F11/70—Control systems characterised by their outputs; Constructional details thereof
    • F24F11/80—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air
    • F24F11/83—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air by controlling the supply of heat-exchange fluids to heat-exchangers
    • F24F11/84—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air by controlling the supply of heat-exchange fluids to heat-exchangers using valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F11/00—Control or safety arrangements
    • F24F11/70—Control systems characterised by their outputs; Constructional details thereof
    • F24F11/80—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air
    • F24F11/87—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air by controlling absorption or discharge of heat in outdoor units
    • F24F11/871—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air by controlling absorption or discharge of heat in outdoor units by controlling outdoor fans
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/30—Expansion means; Dispositions thereof
    • F25B41/31—Expansion valves
    • F25B41/34—Expansion valves with the valve member being actuated by electric means, e.g. by piezoelectric actuators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B49/00—Arrangement or mounting of control or safety devices
    • F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
    • F25B49/027—Condenser control arrangements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F11/00—Control or safety arrangements
    • F24F11/70—Control systems characterised by their outputs; Constructional details thereof
    • F24F11/80—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air
    • F24F11/83—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air by controlling the supply of heat-exchange fluids to heat-exchangers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2600/00—Control issues
    • F25B2600/19—Refrigerant outlet condenser temperature
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
    • Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
    • Y02B30/70—Efficient control or regulation technologies, e.g. for control of refrigerant flow, motor or heating

Definitions

  • the present invention relates to an air conditioning apparatus and a refrigeration cycle control unit for controlling a supercooling degree of liquid refrigerant in the condenser to a predetermined target supercooling degree, by controlling an electric type pressure reducing device of a refrigerant cycle composed of a compressor, a condenser, an electric type pressure reducing device and an evaporator. Furthermore, the present invention relates to a supercooling degree calculating device calculating the aforementioned supercooling degree.
  • a first temperature sensor on a refrigerant pipe at the center of a heat exchanger functioning as a condenser of a refrigerant cycle in order for detecting the temperature of the saturated liquid refrigerant of dryness zero (0), and a second temperature sensor on a refrigerant pipe of the outlet of the condenser are respectively disposed, a supercooling degree of condensed liquid refrigerant in the condenser is calculated from a detected temperature difference of these respective temperature sensors, and an opening degree of an electronic expansion valve is controlled such that the calculated supercooling degree is set to a predetermined value within a certain range.
  • a temperature sensor is generally inferior in its responsibility. Accordingly, as described above, in case that the first temperature sensor detects the temperature of the saturated liquid refrigerant of dryness zero (0), especially when a changing rate of the supercooling degree is large, such as immediately after starting the air conditioner, an error in the detection of the condensed temperature becomes large. Therefore, an error in the calculation of the supercooling degree becomes large, as a result, the control performance of the opening degree of the electronic expansion valve is deteriorated, thus making it impossible to control the supercooling degree accurately.
  • the inventor found out that, if the saturated liquid refrigerant temperature of dryness zero (0) is calculated by using higher responsive pressure sensor than a temperature sensor, the error in the calculation can be small. Therefore, by calculating the supercooling degree based on the saturated liquid refrigerant temperature of dryness zero (0), which has smaller error in the calculation and the outlet refrigerant temperature of the condenser, the error in the calculation of the supercooling degree can be small. The inventor repeatedly examined this matter.
  • the inventor conceived that the saturated liquid refrigerant temperature of dryness zero (0) can be calculated without using a separate sensor specifically, if the discharged pressure sensor disposed at the discharge side of the compressor for protecting from high pressure detects the pressure of discharged refrigerant at the discharge side and calculates the saturated liquid refrigerant temperature of dryness zero (0) from the discharge pressure.
  • outlet refrigerant temperature detected by the outlet refrigerant temperature sensor and the actual refrigerant temperature have a difference due to the ambient temperature of the outlet temperature sensor detecting the outlet refrigerant temperature of the condenser, i.e., in case, for example, the circumference of the outlet temperature sensor is exposed to the outside air, the lower the outside air temperature is, the lower the detected value of the outlet temperature sensor becomes than the actual temperature.
  • an object of the present invention is to reduce an error in the calculation of the supercooling degree calculated from the condensed temperature and the condenser outlet refrigerant temperature small, by reducing an error obtaining the condensed temperature.
  • Another object of the present invention is to calculate the saturated liquid refrigerant temperature of dryness zero (0) with high responsiveness and as accurate as possible in calculating the saturated liquid refrigerant temperature of dryness zero (0) based on a value of the discharge pressure detecting means disposed at the discharge side of the compressor by correcting for this calculated saturated liquid refrigerant temperature corresponding to the portion of the pressure loss of the refrigerant from the position where the discharge pressure detecting means is disposed to the outlet of the condenser.
  • Another object of the present invention is to reduce an error in the detection of the outlet refrigerant temperature and an error in the calculation of the supercooling degree by correcting for the detected value of the detecting means corresponding to the ambient temperature of the means detecting the outlet refrigerant temperature of the condenser.
  • the compressed refrigerant condenses in the condenser. Further, after supercooled, its pressure is reduced by the electric type pressure reducing device. This refrigerant, of which pressure has been reduced, evaporates at the evaporator, then, it returns to the compressor again.
  • control unit controls the electric type pressure reducing device so that the degree of supercooling (supercooling degree) can be set to a predetermined supercooling degree.
  • control unit calculates condensed temperature from high pressure of the refrigerant cycle to calculate the supercooling degree based on this condensed temperature and the outlet refrigerant temperature of the condenser in order to control the electric type pressure reducing device, so that the calculated supercooling degree is set to a predetermined target supercooling degree.
  • an error in obtaining the condensed temperature is reduced as compared with a case where a condensed temperature is obtained by using a temperature detecting means, because pressure detecting means having a higher responsibility than the temperature detecting means is used to calculate the condensed temperature.
  • an error in calculation of the supercooling degree based on the condensed temperature and the outlet refrigerant temperature can be reduced, thereby improving control performance of the electric type pressure reducing device and making it possible to perform an appropriate supercooling degree control.
  • outside air temperature detecting means for detecting the outside air temperature
  • the target supercooling degree calculating means for calculating the target supercooling degree as a larger value in accordance with the decrease of the outside air temperature detected by the outside air temperature detecting means are further included.
  • suction temperature detecting means for detecting suction air temperature of the condenser in the air passage and target supercooling degree calculating means for calculating the target supercooling degree as a larger value in accordance with the decrease of the outside air temperature detected by said suction temperature detecting means are further included.
  • air amount detecting means for detecting air amount passing through the condenser and target supercooling degree calculating means for calculating the target supercooling degree as a larger value in accordance with the increase of the air amount detected by the air amount detecting means are further included.
  • the outside air introducing mode where the inside air inlet is closed and the outside air inlet which is opened is set.
  • the lower the outside air temperature is, the temperature of the air passing through the condenser becomes low.
  • the aforementioned radiated capacity becomes large.
  • the efficiency of the refrigerant cycle can be maximized while optimizing the radiated capacity optimum by calculating the target supercooling degree as a larger value.
  • the larger the air amount passing through the condenser is the lower the high pressure becomes.
  • the target supercooling degree is calculated as a larger value to raise the radiated capacity even if the consumed power becomes large, so that the efficiency of the refrigerant cycle is consequently improved, because the increase of the consumed power can be suppressed within a small value.
  • the larger the air amount of the condenser is the efficiency of the refrigerant cycle can be maximized while optimizing the radiated capacity optimum by calculating the target supercooling degree as a larger value.
  • the high pressure does not abnormally rises at the time of starting the air conditioner and does not deteriorate the efficiency of the refrigerant cycle, but the refrigerant circulation amount can be ensured in addition to the improvement of start-up of the refrigeration cycle, and the supercooling degree can be closer to a target supercooling degree quickly.
  • the condensed temperature is calculated based on a value of the high pressure detecting means, provided originally for high pressure protection and blow air temperature control, so that the high pressure detecting means for calculating the condensed temperature can be easily installed in the vehicle and means only for obtaining the condensed temperature is not needed.
  • FIGS. 1-12 A first embodiment in which the present invention is applied to an automotive air conditioner is described with respect to FIGS. 1-12.
  • An air conditioner duct 2 in an air conditioner unit 1 includes an air passage for introducing the air into a passenger compartment, where an inside/outside air switching means 3 and a blower means 4 are disposed at one end and plural air outlets 14-16 communicating with the passenger compartment are formed at the other end.
  • the inside/outside air switching means 3 includes an inside/outside air switching box, where an inside air inlet 5 for sucking the air (inside air) into the passenger compartment, an outside air inlet 6 for sucking the air (outside air) outside into the passenger compartment are formed.
  • an inside air switching damper 7 is disposed to selectively open or close the respective inlets 5 or 6, and the inside/outside air switching damper 7 is driven by its driving means (not shown, for example, a servomotor).
  • the above blower means 4 generates an air flow in the air conditioner duct 2 from the inside air inlet 5 or the outside air inlet 6 toward the respective air outlets 14-16.
  • a multi-vane fan 9 is disposed in a scroll casing 8, and the fan 9 is driven by a blower motor 10 as its driving means.
  • a cooling indoor heat exchanger 11 is disposed in the air conditioner duct 2 at an air downstream side of the fan 9.
  • the cooling indoor heat exchanger 11 forms a part of a refrigerant cycle 20 and functions as an evaporator dehumidifying and cooling the air in the air conditioner duct 2 by a heat absorbing action of the refrigerant flowing through therein in a cooling operation mode (described below). In the heating operation mode (described below), the refrigerant does not flow through the cooling indoor heat exchanger 11.
  • a heating indoor heat exchanger 12 is disposed in the air conditioner duct 2 at an air downstream side of the cooling indoor exchanger 11.
  • the heating indoor heat exchanger 12 forms a part of a refrigerant cycle 20 and functions as a condenser heating the air in the air conditioner duct 2 in the heating operation mode described below, by a heat radiating action of the refrigerant flowing through therein. In the cooling operation mode (described below), the refrigerant does not flow through the heating indoor heat exchanger 12.
  • an air mixing damper 13 disposed at a position adjacent to the heating indoor heat exchanger 12 regulates an amount of the air supplied from the fan 9 to the heating indoor heat exchanger 12 and the bypass amount of the air supplied from the fan 9 and further flowing so as to bypass the heating indoor heat exchanger 12.
  • the respective air outlets 14-16 there are specifically a defroster air outlet 14 blowing out the air conditioned air toward the inside of the windshield glass of a vehicle, a face air outlet blowing the conditioned air toward the upper half of the body of a passenger in the passenger compartment, and a foot air outlet 16 blowing the conditioned air toward the lower half of the body of the passenger in the passenger compartment.
  • dampers 17-19 are disposed to open/close these outlets 14-16.
  • the above refrigerant cycle 20 is a heat pump type refrigerant cycle for cooling and heating the passenger compartment by the cooling indoor heat exchanger 11 and the heating indoor heat exchanger 12, and includes a refrigerant compressor 21, an outdoor heat exchanger 22, an expansion valve 23 for cooling, an expansion valve 24 for heating, an accumulator 25, a four-way valve 26 for switching the flow of the refrigerant in addition to these heat exchangers 11 and 12, all of which are connected with a refrigerant pipe 27.
  • an electromagnetic valve 28 is disposed to control the flow of the refrigerant
  • an outdoor fan 29 is disposed to blow air toward the outdoor heat exchanger 22.
  • the above outdoor heat exchanger 22 is a heat exchanger functioning as a condenser in the cooling operation mode (described below).
  • the refrigerant compressor 21 sucks, compresses, and discharges the refrigerant when being driven by an electric motor 30.
  • the electric motor 30 is disposed in a sealed case integrally with the refrigerant compressor 21 and its rotational speed continuously varies by the control of an inverter 31.
  • the inverter 31 is supplied with electricity and controlled by a control unit 40 (FIG. 3).
  • both of the expansion valve 23 for cooling and the expansion valve 24 for heating are electric type expansion valves, which changes the valve opening degrees by the control of the electric supply with the control unit 40 (FIG. 3).
  • the relationship of a flowing amount of the refrigerant with respect to the valve opening degree of these expansion valves 23 and 24 is shown in FIG. 2, as for increasing amount of the flowing amount of the refrigerant with respect to the increasing amount of the valve opening degree, it increases with a predetermined inclination from VH2 to ST1 in the control valve 24 for heating, however, it increases with a larger inclination than the inclination from the valve opening degree ST1 to VH1.
  • the control valve 23 for cooling it increases with a predetermined inclination from VC2 to ST1, however, it increases with a larger inclination than the inclination from the valve opening degree ST1 to VC1.
  • the above upper limit value VH1 is determined according to the maximum load in the passenger compartment at the time of heating, whereas the lower limit value VH2 is determined according to the minimum load in the passenger compartment at the time of heating. Furthermore, the upper limit value VC1 described above is determined according to the maximum load in the passenger compartment at the time of cooling, whereas the lower limit value VC2 is determined according to the minimum load in the passenger compartment at the time of cooling.
  • an outside air temperature sensor 41 detecting air temperature of the suction side (more specifically a suction side of the cooling indoor heat exchanger 11) of the heating indoor heat exchanger 12, a discharge pressure sensor 43 detecting refrigerant pressure discharged by the compressor 21, and an outdoor heat exchanger outlet temperature sensor 44 detecting refrigerant temperature after passing through the outdoor heat exchanger 22 are input into the control unit 40.
  • respective signals from an indoor heat exchanger outlet temperature sensor 45 for detecting refrigerant temperature after passing through the heating indoor heat exchanger 12 and a post-evaporator sensor 46 for detecting a cooling degree of the air (more specifically the air temperature immediately after passing the heat exchanger 11) in the cooling indoor heat exchanger 11 are input into the control unit 40, in addition, signals from respective levers and switches of a control panel 51 disposed at the front surface in the passenger compartment are also input.
  • the discharge pressure sensor 43 is disposed on a discharging pipe between the compressor 21 and the four way valve 26.
  • the outdoor heat exchanger outlet temperature sensor 44 is covered with a heat insulating material or the like in order to reduce an error in the detection of the refrigerant temperature.
  • the indoor heat exchanger outlet temperature sensor 45 is covered with a heat insulating material or the like in order to reduce an error in the detection of refrigerant temperature.
  • the control panel 51 is equipped with an outlet mode setting switch 52 for setting respective air outlet modes, an air amount setting switch 53 for setting air amount blown into the passenger compartment, an inside/outside air switching switch 54 setting an inside/outside air switching mode, an operation mode setting switch 55 for setting an operation mode of the refrigerant cycle 20, a temperature setting lever 56 for setting the temperature of the air blown into the passenger compartment, an electric saving switch 57 for setting a saving mode of electric consumption of the electric motor 30, and an automatic switch 58 controlling the inside/outside switching mode, the air amount, the operation mode, the outlet temperature and the air outlet modes.
  • an outlet mode setting switch 52 for setting respective air outlet modes
  • an air amount setting switch 53 for setting air amount blown into the passenger compartment
  • an inside/outside air switching switch 54 setting an inside/outside air switching mode
  • an operation mode setting switch 55 for setting an operation mode of the refrigerant cycle 20
  • a temperature setting lever 56 for setting the temperature of the air blown into the passenger compartment
  • an electric saving switch 57 for setting a saving
  • the operation mode setting switch 55 includes a stop switch 55a for stopping the operation of the compressor 21, a cooler switch 55b for setting the operation mode of the refrigerant cycle 20 to the cooling operation mode, and a heater switch 55c for setting the operation mode of the refrigerant cycle 20 to the heating operation mode, or the like.
  • the temperature setting lever 56 is used when a passenger in the vehicle sets a target outlet temperature of the passenger compartment at a manual operation, and the control unit 40, in accordance with the set position of the lever 56, determines a target value of an air cooling degree (specifically the air temperature immediately after passing through the heat exchanger 11) in the heating indoor heat exchanger 11 in the cooling operation mode. In the heating operation mode, the control unit 40 determines a target value of an air heating degree (discharge refrigerant pressure of the compressor 21) in the heating indoor heat exchanger 12.
  • control unit 40 determines a target rotational speed of the compressor 21 so that the detected value of the discharge pressure sensor 43 is set to the above target value, and controls the inverter 31 according to the target rotational speed.
  • control unit 40 determines the target rotational speed of the compressor 21 so that the detected value of the discharge pressure sensor 43 is set to the above target value, and controls the inverter 31 according to the target rotational speed.
  • the target rotational speed Nc of the compressor 21 is stored in a predetermined area of the RAM.
  • a widely-known microcomputer including CPU, ROM, RAM, or the like (not shown) is incorporated in the control unit 40 so that respective signals from the respective sensors 41-46 and the control panel 51 are input to the above-described microcomputer via an input circuit (not shown) in the ECU.
  • this microcomputer controls the blower motor 10, the expansion valve 23 for cooling, the expansion valve 24 for heating, an electromagnetic valve 28, the outside fan 29, the inverter 31. Furthermore, when the key switch of a vehicle (not shown) is turned on, electric power is supplied from a battery (not shown) to the control unit 40.
  • the microcomputer When a passenger of the vehicle turns on the cooler switch 55b, the microcomputer operates the compressor 21 and controls the four way valve 26 and the electromagnetic valve 28, so that the refrigerant cycle 20 is set to the cooling operation mode. In this mode, the refrigerant flows through the compressor 21, the outdoor heat exchanger 22, the expansion valve 23 for cooling, the cooling indoor heat exchanger 11, the accumulator 25, and the compressor 21 in this order.
  • the microcomputer operates the compressor 21 and controls the four way valve 26 and the electromagnetic valve 28, so that the refrigerant cycle 20 is set to the heating operation mode.
  • the refrigerant flows through the compressor 21, the heating indoor heat exchanger 12, the expansion valve 24 for heating, the outdoor heat exchanger 22, the electromagnetic valve 28, the accumulator 25, and the compressor 21.
  • the routines of FIGS. 5-8 start, at the first step 110, an initializing step for resetting all flag "f", timers T1 and T2 or the like, which will be used in the subsequent process, is performed. Then, at the step 120, signals from the respective sensors 41-46 and the respective levers and switches of the control panel 51 are read in.
  • the step 130 based on a signal from the operation mode setting switch 55, it is determined whether the operation mode of the refrigerant cycle 20 has changed or not.
  • the flag "f" is reset at the step 140, however, in case of NO (there is no change), it proceeds to the step 150, and it is determined whether or not the operation mode is set to the heating operation mode by checking whether the heater switch 55c is on or not.
  • the opening degree of the expansion valve 23 for cooling (hereinafter referred to EVC) becomes zero at the next step 160, that is, the expansion valve 23 is fully closed. Then, by determining whether or not the flag "f" is set at the step 170, it is determined whether or the steps 180-200 described below have been already performed or not.
  • the opening degree of the expansion valve 24 for heating (hereinafter, referred to EVH) is maintained at the previously set upper limit value VH1 by a certain time ⁇ 1 set in advance.
  • the above-specified time ⁇ 1 is set as a period of the compressor 21 to decrease to a certain extent, of which load is already large enough at the initial time of starting the air conditioner.
  • the above EVH is set to the above-mentioned upper limit value VH1 at the step 180. Then, at the next step 190, it counts up the timer T1, and at the next step 200, it is determined whether or not the timer T1 exceeds the aforementioned time ⁇ 1 . When it does not exceed the time ⁇ 1 , it returns to the step 290 again, however, when it exceeds the time ⁇ 1 , it moves to the step 220 after the flag "f" is set at the step 210.
  • SC a supercooling degree (hereinafter, referred to SC) of the condensed liquid refrigerant in the heating indoor heat exchanger 12 is described, based on the following equation (1).
  • SC T (Pd) - T cs
  • T (Pd) represents condensed temperature calculated by the detected value of the discharge pressure sensor 43
  • T cs represents a detected value of the interior heat exchanger outlet temperature sensor 45.
  • discharge refrigerant pressure detected by the discharge pressure sensor 43 is pressure at a point "A" in the Mollier chart (FIG. 7) of the refrigerant cycle 20. Namely, it is substantially the same as the pressure at a point "B".
  • the present embodiment based on a map showing the relationship (not shown) between the condensed refrigerant pressure and the condensed temperature, which is stored in the ROM, obtains the condensed temperature at the point "B". This is the above-described T (Pd).
  • the refrigerant temperature detected by the indoor heat exchanger outlet temperature sensor 45 is the refrigerant temperature at a point "C" in FIG. 7. Accordingly in this embodiment, by performing the calculation with the above equation (1), the difference between the refrigerant temperature at the point "B” and the refrigerant temperature at the point "C" in FIG. 7, i.e., SC, is calculated.
  • a target temperature of the supercooling degree (hereinafter referred to SCO) is calculated so that the efficiency of the refrigerant cycle 20 is maximized in order to save the electricity.
  • SCO a target temperature of the supercooling degree
  • the outside air introducing mode is set to prevent the windows from being defrosted. Therefore, in this case, the lower the outside air temperature becomes, the lower the air temperature at the suction side of the heating indoor heat exchanger 12 becomes. That is, the air temperature passing through this heat exchanger 12 becomes low.
  • the air temperature passing through the heat exchanger 12 is low means that a temperature difference between the refrigerant temperature in the heat exchanger 12 and the temperature of the passing air is large, i.e., it means the radiated capacity Q is large.
  • SCO is calculated as a larger value, and as a result, even if the power W becomes consequently large, since the capacity Q becomes larger than that and the heating COP becomes large, so that when the outside air temperature or the suction temperature is low as described above, SCO is calculated as a larger value compared with a case when these temperatures are high.
  • increasing/decreasing opening degree ⁇ EVH of the expansion valve 24 for heating corresponding to the above deviation ⁇ SC is calculated.
  • the upper limit value EVH1 and the lower limit value EVH2 of ⁇ EVH are determined to prevent the hunting of SC.
  • the opening degree of the expansion valve 24 for heating is increased or decreased by the above ⁇ EVH. Then, at the step 270, it counts up the timer T2, and at the next step 280, it is determined whether or not the timer T2 has exceeded a preset time ⁇ 2 . When it has not exceeded the preset time ⁇ 2 , it returns to the step 270 again, however, when it has exceeded, it returns to the step 120.
  • the determination is NO at the above step 150, it jumps to the step 290 of FIG. 6, and by checking whether or not the cooler switch 55b is turned on, it is determined whether or nor the operation mode is the cooling operation mode.
  • the determination is NO, i.e., when the both cooling switch 55b and the heater switch 55c are not turned on, it returns to the step 120 of FIG. 5, however, when the determination is YES, at the following step 300, the opening degree EVH of the expansion valve 24 for heating is set to 0. Namely, the expansion valve 24 for heating is fully closed.
  • the flag "f" By determining whether or not the flag "f" is set at the step 310, it is determined whether or not the steps 320-340 described below have been already performed. In this case, when the flag "f" is set, i.e., it determines that the steps 320-340 have been already performed, it directly jumps to the step 360, however, when it determines that these steps 320-340 have not been performed yet, the opening degree EVC of the expansion valve 23 for cooling is maintained at the upper limit value VC1 by the time ⁇ 1 .
  • the step 320 sets EVC to the aforementioned upper limit value VC1.
  • it counts up the timer T1, and at the following step 340, it is determined whether or not the timer T1 has exceeded the time ⁇ 1.
  • it determines that the timer T1 has not exceeded the time ⁇ 1, it returns to the step 330 again, however, when it determines that the timer T1 has exceeded the time ⁇ 1, after the flag "f" is set at the step 350, it moves to the step 360.
  • the supercooling degree SC of the condensed liquid refrigerant in the indoor heat exchanger 22 is calculated based on the following equation (2).
  • SC T (Pd) - T OS wherein T OS represents a detected value of the outdoor heat exchanger outlet temperature sensor 44.
  • a target value SCO of the supercooling degree is calculated.
  • the SCO is also determined based on the same concept as in the determination at the step 230.
  • the SCO is calculated as a larger value.
  • increasing/decreasing opening degree ⁇ EVC of the expansion valve 23 for cooling corresponding to the deviation ⁇ SC is calculated.
  • the degree of the expansion valve 23 for cooling by the ⁇ EVC is increased or decreased. Then, at the step 410, it counts up the timer T2, and at the next step 420, it is determined whether or not the timer T2 has exceeded a preset time ⁇ 2 . When it is determined that it has not exceeded the preset time ⁇ 2 , it returns to the step 410 again, however, when it is determined that it has exceeded, it returns to the step 120.
  • the valve opening degree EVH of the expansion valve 24 for heating is fixed to VH1.
  • a target supercooling degree SCO is calculated, however, in an example of this FIG. 12, the supercooling degree SC at the point “t 1 " is smaller than the above-specified SCO and ⁇ SC becomes a negative value, so that ⁇ EVH also becomes a negative value judging from FIG. 9.
  • the EVH gradually becomes smaller, however, SC gradually increases. Then, EVH becomes smaller by the ⁇ EVH at the "t 2 " after the time ⁇ 2 .
  • condensed temperature is calculated based on the signal from a high responsive pressure sensor (discharge pressure sensor 43) compared with a temperature sensor, an error to obtain the condensed temperature can be smaller in comparison with a case where the condensed temperature is directly detected by the temperature sensor. Accordingly, in this embodiment, since the calculation error of the supercooling degree SE is reduced, control performance of an electric type pressure reducing device can be improved, thus making it possible to perform an appropriate control of the supercooling degree.
  • the condensed temperature is calculated based on the signal from the discharge pressure sensor 43 disposed between the compressor 21 and the four way valve 26, even in case both the cooling and the heating operations are performed by using the heat pump type refrigerant cycle as in this embodiment, the condensed temperature can be calculated from the signal of the same discharge pressure sensor 43, so that the number of parts can be reduced compared with a case where respective sensors for detecting the condensed temperature are disposed at a condenser (the outdoor heat changer 22) in the cooling operation mode and at a condenser (the heating indoor heat exchanger 12) in the heating operation mode.
  • the condensed temperature is essentially calculated based on the signal from the discharge pressure sensor 43, which is provided originally for high pressure protection and blowing air temperature control, so that another pressure sensor only for calculating the condensed temperature is not needed separately.
  • an opening degree of the expansion valve is fixed to VH1 or VC1 in such a manner that a larger opening degree than ordinary is set (practically fully opened). Therefore, at the time of starting the air conditioner, an abnormal rise of high pressure is prevented, the efficiency of the refrigerant cycle 20 is prevented from being deteriorated, and furthermore, circulating amount of the refrigerant can be ensured, thus resulting in improvement of the start-up of the refrigerant cycle 20 and making SC close to a target value quickly.
  • the upper limit value VH1 (or VC1) and the lower limit value VH2 (or VC2) of the opening degree of the expansion valve can be changed depending on an environmental condition. For example, when a load within the passenger compartment is large, the upper limit value VH1 (VC1) may be a larger value compared with a small load, and also VH2 (or VC2) may be made larger according to this.
  • the times ⁇ 1 and ⁇ 2 may be changed depending on an environmental condition. For example, when a load within the passenger compartment is large at the initial time to start the air conditioner, the time ⁇ 1 may be made larger than a small load, and also when ⁇ EVH is large, the time ⁇ 2 may be made larger than small ⁇ EVH.
  • the SCO may be calculated as a larger value.
  • the SCO may be calculated as a higher value.
  • FIGS. 13-15 A second embodiment of the present invention is described with respect to FIGS. 13-15.
  • the supercooling degree SC of the condensed liquid refrigerant in the heating indoor heat exchanger 12 at the step 220 in FIG. 5 and the target value SCO of the supercooling degree at the step 370 in FIG. 6 are calculated as follows.
  • a pressure loss ⁇ Pc of the refrigerant from the position where the discharge pressure sensor 43 is disposed to the position where the indoor heat exchanger outlet temperature sensor 45 is disposed by substituting the target rotation speed Nc of the compressor 21 stored in RAM and the detected value Tos of the outdoor heat exchanger outlet temperature sensor 44 read in at the step 120 for the following equation (3).
  • the pressure loss ⁇ Pc is a difference between the refrigerant pressure at the point "C” and the refrigerant pressure at the point “B” in the Mollier chart of the refrigerant cycle 20 shown in FIG. 15.
  • the pressure at the point "C” is a refrigerant pressure at the position where the interior heat exchanger outlet temperature sensor 45 is disposed in case the above-described ⁇ Pc is taken into account.
  • ⁇ Pc A ⁇ Nc m ⁇ Tos n
  • the equation (3) is an approximate equation obtained by an experiment.
  • the above “A”, “m”, and “n” are experimental constants, respectively.
  • m is set to be larger than zero (m > 0) so that the higher the rotation speed Nc becomes, the larger the pressure loss ⁇ Pc becomes, that is, the lower the rotational speed Nc becomes, the smaller the pressure loss ⁇ Pc becomes.
  • n is set to be larger than 0 so that the higher the outlet temperature Tos becomes, the larger the pressure loss ⁇ Pc becomes, that is, the lower the outlet temperature Tos becomes, the smaller the pressure loss ⁇ Pc becomes.
  • the higher the rotational speed Nc of the compressor 21 becomes the higher the rotational speed Nc of the compressor 21 becomes, the larger the flowing amount of the refrigerant circulating in the refrigerant cycle and the flowing speed of the refrigerant at the high pressure side of the refrigerant cycle 21 becomes fast, which causes larger pressure loss at the high pressure side. Therefore, in the second embodiment, the higher the rotational speed of the compressor becomes, the larger the pressure loss ⁇ Pc is, whereas, the smaller the pressure loss ⁇ Pc is, the lower the rotational speed Nc becomes.
  • the higher the outlet temperature Tos becomes that is, the higher the pressure of the refrigerant at the low pressure side of the refrigerant cycle 20 becomes, the larger the specific gravity of the refrigerant becomes and the larger the weight flowing amount of the refrigerant flowing at the high pressure side of the refrigerant cycle 21, which causes large pressure loss at this high pressure side.
  • the higher the outlet temperature Tos becomes the larger the pressure loss ⁇ Pc is, whereas, the lower the outlet temperature Tos becomes, the smaller the pressure loss ⁇ Pc is.
  • an outlet refrigerant pressure Pc pressure at the point "C" of FIG. 15
  • the supercooling degree SC of the condensed liquid refrigerant in the heating indoor heat exchanger 12 is calculated, based on the following equation (4).
  • temperature Tc' (temperature at the point "D") of saturated liquid refrigerant of dryness zero (0) in the heating indoor heat exchanger 12 corresponding to the above-described outlet refrigerant pressure Pc (pressure at the point "C") is calculated by searching from the map (not shown) showing the relationship between the refrigerant pressure and the saturated liquid refrigerant temperature of dryness zero (0), which is stored in ROM.
  • the refrigerant is in a state of supercooled liquid from the point "D" to the point "C".
  • the refrigerant pressure at the point "C” and the refrigerant pressure at the point “D” can be regarded as equal.
  • the temperature Tc' is equal to Tc' which is calculated from the pressure of the point "D".
  • a difference between the detected outlet refrigerant temperature Tcs and the actual outlet refrigerant temperature is calculated as a correction value ⁇ Tc by substituting the detected value of the outside air temperature sensor 41 and the outlet refrigerant temperature Tcs (refrigerant temperature at the point "C" of FIG. 15) detected by the indoor heat exchanger outlet temperature sensor 45 with the following equation (5).
  • ⁇ Tc a ⁇ (Tcs - Tam)
  • the equation (5) is an approximate equation obtained by an experiment.
  • the "a” is an experimental constant.
  • more accurate outlet refrigerant temperature is calculated as correction outlet refrigerant temperature Tc based on the following equation (6) by adding the correction value ⁇ Tc calculated at the detected outlet refrigerant temperature Tcs.
  • Tc Tcs + ⁇ Tc
  • the correction outlet refrigerant temperature Tc obtained by the above equation (6) becomes higher than the detected outlet refrigerant temperature Tcs when the outside temperature Tam becomes lower, on the other hand, when the outside temperature becomes higher, its temperature becomes closer to the detected outlet refrigerant temperature Tcs.
  • the above supercooling degree SC is calculated by substituting the temperature Tc' (temperature at the point "D") of the saturated liquid refrigerant calculated at the step 223 and the correction outlet refrigerant temperature Tc (Temperature at the point "C") calculated at the step 225 with the following equation (7).
  • SC Tc' - Tc
  • the supercooling degree SC of the condensed liquid refrigerant in the outside heat exchanger 22 is calculated.
  • the pressure loss ⁇ Po of the refrigerant from the position where the discharge pressure sensor 43 is disposed to the position where the outdoor heat exchanger outlet temperature sensor 44 is disposed is calculated by substituting the aforementioned rotation speed Nc of the compressor contained in RAM and the detected value Te of the post evaporator sensor 46 read in at the step 120 with the following equation (8).
  • the pressure loss ⁇ Po is a difference between the pressure B and the pressure at the point "C" of FIG. 15 in the same manner as in the heating operation mode.
  • ⁇ Po B ⁇ Nc k ⁇ Te l
  • the equation (8) is an approximate equation obtained by an experiment.
  • the "B”, “k”, and “l” are experimental constants, respectively.
  • k is set to be larger than zero (k > 0) so that the higher the rotation speed Nc can become, the larger the pressure loss ⁇ Pc becomes, that is, the lower the rotation speed Nc becomes, the smaller the pressure loss ⁇ Pc becomes.
  • l is set to be larger than zero (0) so that the higher the temperature Te becomes, the larger the pressure loss ⁇ Pc becomes, that is, the lower the temperature Te becomes, the smaller the pressure loss ⁇ Pc becomes. Since the reason is the same as in the heating operation mode, the explanation is omitted.
  • the outlet refrigerant pressure Po pressure at the point "C" of FIG. 9 in the position where the outdoor heat exchanger outlet temperature sensor 44 is disposed is calculated by substituting a detected value Pd of the discharged pressure sensor 43 and the pressure loss ⁇ Po with the following equation (7).
  • a difference between this detected outlet refrigerant temperature Tos and the actual outlet refrigerant temperature is calculated as a correction value ⁇ To by substituting the detected value Tam of the outside air temperature sensor 41 and the outlet refrigerant temperature Tcs (refrigerant temperature at the point "C" of FIG. 15) detected by the outdoor heat exchanger outlet temperature sensor 44 with the following equation (8).
  • ⁇ To b ⁇ (Tos - Tam)
  • This equation (8) is an approximate equation obtained by an experiment.
  • the "b” is an experimental constant.
  • the supercooling degree SC is calculated by substituting the saturated liquid refrigerant temperature To7 (temperature at the point “D") calculated at the step 363 and the correction outlet refrigerant temperature To (temperature at the point “C") calculated at the step 365 with the following equation (12).
  • SC To' - To
  • An error in the calculation of the supercooling degree SC calculated by a difference between the saturated liquid refrigerant temperature Tc' (or To') and the outlet refrigerant temperature Tc (or To) at the position where the outlet temperature sensor 45 (44) is disposed can be reduced, thereby improving the control performance of the expansion valve 24 (or 23) and making it possible to perform an appropriate control of the supercooling degree.
  • the outlet refrigerant temperature Tc (or To) is obtained by compensating temperature Tcs (or Tos) detected by the outlet temperature sensor 45 (or 44) corresponding to the outside air temperature, the outlet refrigerant temperature can be more accurately obtained. Accordingly, the error in the calculation of the supercooling degree SC is reduced, control performance of the expansion valve 24 (or 23) is improved, and furthermore, an appropriate control of the supercooling degree can be performed.
  • the temperature of the refrigerant flowing in the heat exchanger functioning as an evaporator is detected by an outdoor heat exchanger outlet temperature sensor 44 in the heating operating mode and by the post evaporator sensor 46 in the cooling operation mode, however, the pressure of the refrigerant flowing in this heat exchanger may be employed.
  • the rotational speed detecting means is composed of RAM, however, a sensor for directly detecting the rotation speed of the compressor 21 is provided and this sensor may be employed as the rotational speed detecting means.
  • a heat pump type refrigerant cycle is employed, however, the refrigerant cycle may be made of a single cooler or single heater.
  • the present invention is applied to an air conditioner for an electric vehicle, however, it may be applied to an air conditioner for a vehicle driven by an engine as well as an air conditioner for a room in a housing or building.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Signal Processing (AREA)
  • Fuzzy Systems (AREA)
  • Mathematical Physics (AREA)
  • Fluid Mechanics (AREA)
  • Air Conditioning Control Device (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
  • Air-Conditioning For Vehicles (AREA)
EP96110225A 1995-06-26 1996-06-25 Klimaanlage Expired - Lifetime EP0751356B1 (de)

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JP15959395A JP3063574B2 (ja) 1995-06-26 1995-06-26 空調装置
JP159593/95 1995-06-26
JP15959395 1995-06-26
JP16055795A JP3063575B2 (ja) 1995-06-27 1995-06-27 冷凍サイクル制御装置
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EP1887292A1 (de) * 2005-05-30 2008-02-13 Daikin Industries, Ltd. Feuchtigkeitsregler
EP1887292A4 (de) * 2005-05-30 2009-04-08 Daikin Ind Ltd Feuchtigkeitsregler
CN101913314A (zh) * 2010-07-30 2010-12-15 奇瑞汽车股份有限公司 一种电动汽车空调系统及其控制方法
CN103162328A (zh) * 2011-12-19 2013-06-19 松下电器产业株式会社 热水供暖装置
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CN103162328B (zh) * 2011-12-19 2016-09-07 松下电器产业株式会社 热水供暖装置
CN104883005A (zh) * 2015-06-11 2015-09-02 广东美的暖通设备有限公司 电机散热结构、空调器和电机散热方法
CN109945564A (zh) * 2019-03-22 2019-06-28 广东美的制冷设备有限公司 多联机系统及其压缩机的回油方法和回油装置
CN109945564B (zh) * 2019-03-22 2021-12-21 广东美的制冷设备有限公司 多联机系统及其压缩机的回油方法和回油装置

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US5701753A (en) 1997-12-30
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DE69626069T2 (de) 2003-06-12
EP0751356B1 (de) 2003-02-05

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